|Publication number||US8066602 B2|
|Application number||US 12/642,113|
|Publication date||29 Nov 2011|
|Filing date||18 Dec 2009|
|Priority date||6 Nov 2001|
|Also published as||DE60217611D1, DE60217611T2, EP1308646A2, EP1308646A3, EP1308646B1, EP1722131A2, EP1722131A3, EP1722131B1, US7125356, US7654925, US20030087714, US20060240925, US20100151978|
|Publication number||12642113, 642113, US 8066602 B2, US 8066602B2, US-B2-8066602, US8066602 B2, US8066602B2|
|Inventors||Kevin B. Todd|
|Original Assignee||Borgwarner Inc.|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (118), Non-Patent Citations (21), Referenced by (4), Classifications (8), Legal Events (2)|
|External Links: USPTO, USPTO Assignment, Espacenet|
This application is a continuation of prior application Ser. No. 11/456,496, filed Jul. 10, 2006 now U.S. Pat. No. 7,654,925, which is a continuation of prior application Ser. No. 09/993,531, filed Nov. 6, 2001, now U.S. Pat. No. 7,125,356 B2, which are hereby incorporated herein by reference in their entirety.
The invention relates generally to a sprocket, and particularly to a sprocket for reducing chain tensions.
Chain and sprocket systems are often used in automotive engine systems to transmit rotational forces between shafts. For example, a sprocket on a driven shaft may be connected via a chain to a sprocket on an idler shaft. In such a chain and sprocket system, rotation of the driven shaft and driven sprocket will cause the rotation of the idler shaft and idler sprocket via the chain. In an automotive engine system, sprockets on the crankshaft may be used, for example, to drive one or more cam shaft sprockets.
The chains used in chain and sprocket systems typically comprise a plurality of intermeshing link plates connected with pins or rollers. The sprockets typically comprise a circular plate having a plurality of teeth disposed around the circumference thereof. Located between adjacent teeth are roots having generally arcuate or semi-circular profiles for receiving the pins or rollers of the chain. Each root has a root radius, defined as the distance from the center of the sprocket to a point on the root closest to the sprocket center.
In a “straight” sprocket the root radii are all substantially equal. However, it has been found that as a chain rotates around a straight sprocket, audible sound frequencies creating undesirable noise are often generated as the pins or rollers connecting the links of the chain contact the sprocket teeth and impact the roots disposed between adjacent teeth of the sprockets.
The sound frequencies and volume of such noise typically varies depending on the chain and sprocket designs, chain rotational speed, and other sound or noise sources in the operating environment. In the design of chain and sprocket systems, it can be desirable to reduce the noise levels generated as the rollers of a chain engage roots of a sprocket.
“Random” sprockets have been developed to help reduce the radiated noise levels generated by the engagement of the chains with the sprockets. Random sprockets may be characterized by having a plurality of different root radii. The different root radii can be arranged in a pattern around the sprocket circumference to modulate the sound frequencies generated by the engagement of the chain rollers or pins with sprocket teeth and roots. By modulating these sound frequencies, the noise generated as the chain rotates around the sprocket may be reduced.
In addition to minimizing noise generated by engagement between a chain and sprocket, it is also desirable to reduce the tensions imparted to the chain by the sprocket. Reduced chain tensions can be advantageous because they may result in decreased wear of the chain, thus increasing the life cycle of the chain. Furthermore, reduced chain tensions may also result in less wear to the sprocket, thereby also increasing the life cycle of the sprocket.
It has been observed in chain tension measurements that certain chain tensions in a particular system may vary on a periodic or repeating basis, which often can be correlated to tension inducing events. For example, in automotive timing chain systems, it has been observed from chain tension measurements that the engagement and disengagement of each sprocket tooth and/or root with the chain pins often results in repeating tension changes. These chain tension changes may be correlated with potentially tension inducing events, such as the firing of piston cylinders, transmission engagements, etc.
A useful approach to analyzing such tension events is to observe the number of events that occur relative to a reference time period, as well as the amount of the tension change for each event. For example, in an automotive timing chain system, one may observe the number or frequency of tension changes in the chain relative to rotations of a sprocket or a crankshaft, as well as the magnitude of the tension change in the chain.
In such a system, for example, a tensioning event that occurs once per shaft or sprocket rotation may be considered a “first” order event, and an event occurring four times for each shaft or sprocket rotation may be considered a “fourth” order event. Depending on the system and the relative reference period, i.e., rotations of the crankshaft or the sprocket (or another reference), there may be multiple “orders” of events in a crankshaft or sprocket rotation in such a system originating from one or more tension sources. Similarly, a particular order of the sprocket rotation may include or reflect the cumulative effect of more than one tensioning event. As used herein, such orders of tensioning events occurring during a sprocket (or crankshaft) rotation also may be referred to as the orders of a sprocket (or crankshaft) and/or sprocket orders (or crankshaft orders).
In straight sprockets, measurable tensions typically are imparted to the chain at a sprocket order corresponding to the number of teeth on the sprocket, also known as the pitch order. Thus, in a sprocket with nineteen teeth, tensions would be imparted to the chain at the nineteenth or pitch order, i.e., nineteen times per revolution of the sprocket. Depending on the sprocket design, the order in a straight sprocket would typically occur at equal intervals relative to the sprocket rotation, with a generally equal tension change or amplitude.
Random sprockets, in contrast, typically have different tensioning characteristics when compared to straight sprockets due to the different root radii. As the chain rotates around the random sprocket, each of the different root radii typically imparts a different tensioning event to the chain. For instance, as a roller of the chain engages a root having a first root radius, the chain may be imparted with a tension different from when a roller of the chain engages a root having a second root radius larger than the first root radius. Tension changes, in addition, may also be imparted to the chain by a random sprocket due to the relative positioning of the different root radii. A roller moving between adjacent roots having the same root radii may result in different chain tension changes than a roller moving between adjacent roots having different radii.
The change in chain tensions imparted by random sprockets may be further accentuated when the sprocket has more than two different root radii. In a random sprocket having first, second, and third successively larger root radii, the tension imparted to the chain may be greater when a chain roller moves from a root having a first root radii to a root having a third root radii than when a chain roller moves from a root having a first root radii to a root having a second root radii.
Thus, random sprockets designed principally for noise reduction often cause increases in chain tensions and tension changes as compared to the maximum tensions imparted to the chain by straight sprockets. For example, a random sprocket design may reduce chain noise or chain whine by reducing the pitch order of the sprocket. However, reducing the pitch order of a sprocket may result in redistributing or concentrating the tensional forces imparted to the chain by the sprocket over the lower orders of the sprocket. This often results in increased chain tensions corresponding to the lower orders of the random sprocket.
The increased chain tensions at the lower sprocket orders frequently cause the overall maximum chain tension force exerted on the chain and sprocket to increase. As a consequence, a chain and sprocket system subjected to such tensions typically will experience greater wear and increased opportunities for failure, as well as others adverse effects, due to the concentration of the tensional forces in the lower orders.
Accordingly, there remains a need for a sprocket design and method of designing sprockets that incorporates the noise reduction properties of random sprockets without the increased maximum chain tensions associated therewith. In addition, there is a need for a sprocket design and method for designing sprockets to provide the flexibility to shift tensional forces to different sprocket (or other) orders to enhance the performance, durability, and efficiency of a chain and sprocket system or other comparable systems.
In accordance with one aspect of the invention, a sprocket is provided that has a root pattern and root radii selected to concentrate the maximum chain tensions at a predetermined order or at multiple predetermined orders relative to the sprocket rotation or another reference, such as, for example, the rotation of a crankshaft in automatic timing chain applications. In this aspect, a sprocket is provided that promotes reduced or controlled chain tensions and may also simultaneously reduce chain noise.
In another important aspect, the order or orders of the sprocket having the concentrated chain tensions may be chosen to at least partially cancel or add to corresponding tensions imparted to the chain from sources external to the sprocket. By coordinating the maximum tensions imparted to the chain by the sprocket with the maximum or minimum tensions imparted to the chain by sources external to the sprocket, the overall maximum tensions in the system may be reduced or redistributed in a beneficial way.
In another important aspect of the invention, a sprocket is provided that has a random tooth pattern and root radii that are selected to concentrate the maximum chain tensions at a predetermined order of the sprocket (or other reference). The sprocket comprises a plurality of radially extending teeth arranged around the circumference of the sprocket. Roots are defined between adjacent teeth and have a generally concave or semi-circular profile for engagement with roller or pin connecting links of the chain. The roots each have a root radius measured from the center of the sprocket to a point along the root closest to the sprocket center in the radial direction.
In accordance with another aspect of the invention, the tooth pattern of the random sprocket may comprise two or more different root radii between adjacent teeth arranged in a predetermined pattern around the circumference of the sprocket effective to reduce the sound frequencies generated as the rollers of the chain engage the sprocket teeth and roots, and the overall tension forces in the chain and sprocket system. In another important aspect of the invention, three different root radii may be arranged in a pattern around the circumference of the sprocket. The use of three different root radii to vary the depth of the spaces between adjacent teeth may further reduce the sound frequencies and overall tension forces exerted on the system.
The root radii pattern according to the sprocket of another aspect of the invention also may be selected to redistribute the first, second, third, and fourth order tensions imparted to the chain by the sprocket to a fourth order of the sprocket revolution. In yet another aspect of the invention, a sprocket is provided that reduces chain tensions and chain noise, as compared to typical random sprockets designed principally for noise reduction.
In still another aspect of the invention, the maximum tensions imparted to the chain by the sprocket may be concentrated at the fourth order of the sprocket rotation. Accordingly, a peak in the chain tension imparted by the sprocket occurs four times for every rotation of the sprocket.
According to another aspect of the invention, the sprocket may be used in a chain and sprocket system where tension is imparted to the chain from sources external to the sprocket. When the maximum tensions imparted to the chain from sources external to the sprocket occur at generally predetermined orders of the sprocket rotation, the arrangement of the sprocket root radii may be selected to at least partially offset, disperse, compensate for, or add to the tensions imparted to the chain originating from external sources.
In another aspect of the invention, a random sprocket may comprise a plurality of different pitch radii, as measured from the center of the sprocket to a chain joint when the chain is seated in the sprocket. The plurality of different pitch radii may be arranged in a pattern effective to distribute chain tensions at one or more predetermined orders of the sprocket revolution, such as for silent chains wherein teeth of the chain contact teeth of the sprocket.
The invention in one important aspect is embodied in a random sprocket for use in an automotive chain and sprocket system, such as used in an engine timing system. In this aspect of the invention, the sprocket root radii and patterns are selected, and are effective, to redistribute chain tensions to one or more predetermined orders of the sprocket revolution. In another important aspect, the random sprocket has a plurality of different root radii arranged in a pattern effective to reduce tensions imparted to the chain by the sprocket. In yet another aspect, the root radii and pattern is selected to reduce tensions important to the chain and to reduce noise generated as the chain contacts the sprocket.
Sprocket roots 14 are defined between adjacent teeth 12 for receiving pins or rollers 84 that connect the links 82 of the chain 80. The roots 14 have a generally arcuate profile to facilitate engagement with the pins 84 of the chain. Each root 14 has a root radius RR, defined as the distance from the center of the sprocket 10 to a point along the root 14 closest to the sprocket center. In the illustrated sprocket 10, the root radius RR is approximately 2.57685 cm, as measured from the center of the sprocket 10 to the innermost point along the root 14. The sprocket 10 of
Different tensioning events of the chain 80 may be repeated on a periodic basis during each rotation of the sprocket 10. As mentioned above, the number of times a given tensioning event is repeated in one rotation of the sprocket 10 may be referred to as an “order” relative to the sprocket 10 rotation. For example, a tensioning event of the chain 80 that occurs once during each rotation of the sprocket 10 may be termed a first order event, events occurring twice during one sprocket revolution may be termed second order events, etc.
When the tension in the chain 80 is observed during operation of the system, increases in the tension of the chain 80 may occur at certain orders of the sprocket 10 revolution. In a straight sprocket, such as the sprocket 10 of
Thus, a chain rotating about the sprocket 10, having nineteen teeth 12, will have a peak in the tension imparted to the chain 80 by the sprocket at the nineteenth order of the sprocket revolution, or nineteen times for every revolution of the sprocket 10. Peaks in the tension imparted to a chain 80 by a sprocket 10 may also be due to other factors besides the number of sprocket teeth 12. For example, a sprocket 10 that is not rotating about its exact center may impart a tension to the chain 80 at the first sprocket order, or once for every rotation of the sprocket 10, due to the eccentric rotation of the sprocket 10.
In order to reduce noise generated by contact between pins or rollers 84 of a chain 80, and roots 14 and teeth 12 of a sprocket 10, “random” sprockets have been developed with plurality of different root radii. For example, a random sprocket may have two different root radii arranged in a predetermined pattern selected to decrease noise. A random sprocket may also be designed to incorporate three different root radii arranged in a predetermined pattern to further reduce noise generated by engagement of the chain 80 with the sprocket. The root radii may vary based on the particular system and sprocket design.
The random sprocket 20 illustrated in
The root depths 1-3 are arranged in a pattern selected to modulate the engagement frequency between the pins 84 of the chain 80 and roots 24 between adjacent teeth 22 of the sprocket 20 in order to reduce noise generation. As the pins 84 of the chain 80 move between adjacent roots 24 of the sprocket 22, the radial position at which the pins 84 seat varies between a maximum radius, a nominal radius, and a minimum radius. In the noise reducing sprocket 20 of
The sprocket 20 was mounted on a shaft and used to drive a chain 80. A tension measuring device was placed in contact with the chain 80 to measure the tension as the chain 80 was driven by the sprocket 20.
Thus, in the random sprocket 20 having three different root radii arranged in pattern selected for noise reduction, illustrated in
In order to reduce the chain tensions resulting from random sprockets such as in Example 1, the tensions imparted to the chain 80 by a sprocket utilizing one aspect of the invention may be redistributed among select sprocket orders or concentrated at a predetermined sprocket order. In this aspect, a plurality of different root radii are used and those root radii are arranged in one or more patterns that are effective to redistribute chain tensions occurring at one or more sprocket orders to other sprocket orders. The root radii and patterns also may be selected to reduce chain noise or whine without the disadvantages of random sprockets such as those discussed above and in Example 1.
In this aspect, the sprocket root radii are selected relative to a maximum radius and a minimum root radius as determined from the chain link size and configuration; the chain connecting pin size and spacing; and/or the number of sprocket teeth, tooth configuration and sprockets size. The root radii also may be selected relative to a nominal root radius which typically is the mid-point between the maximum and minimum root radii, and often is analogous to the root radii selected for a similar straight sprocket.
The selection of varying root radii allows for the distribution of the pitch tensions generated by the chain to sprocket tooth/root contact. It is believed that this is due to the contact of the chain pins (or equivalent chain elements) with the sprocket teeth/roots at different times and at different tension levels as a result of the varying depths of the sprocket roots.
The root radii further are arranged in a pattern that repeats around the sprocket circumference. This pattern typically includes one or more sets or multiple, non-uniform or random root radii. Each set typically includes the same number of root radii having the same length and arranged in the same order. Different sets of root radii may have radii of different lengths, number and arrangement.
The use of such patterns of sets of otherwise random root radii repeated along the circumference of the sprocket permits the shifting of those tensions to specific sprocket orders (or other orders based on the applicable reference). In doing so, the cumulative effect of shifting the tension forces permits the planned reduction or increase in the amount of chain tension is incorporated to the system by the sprocket at specific sprocket orders (or other reference orders).
The selection of the patterns of non-uniform or random root radii, and the lengths of those radii further permits the use of major and minor patterns or sub-patterns of root radii. Such major and minor patterns are effective to redistribute the tensions imparted to the chain (and overall system) to multiple sprocket orders (or other applicable orders) and at different magnitudes. This provides the additional flexibility in the selection of the sprocket root radii and patterns to offset multiple tension sources in the system and/or to balance the overall tensions on the chain and sprocket regardless of other sources of the tensional forces.
Moreover, the selection of such root radii and patterns permits the design of a sprocket and chain system that provides reduced levels of chain noise with the proper selection of the root radii within a set of radii, without unduly increasing overall chain or system tensions. Similarly, such a design is capable of providing reduced chain noise life and durability of the chain and a balance of tensional forces extending the sprocket system.
The following Example 2 illustrates several important aspects of the invention. Other variations and applications of the invention also are discussed below.
The sprocket 30 of
As illustrated in
Thus, the use of a random pattern of root radii grouped in sets of radii in this example provide a repeating pattern which may be used to effectively shift and concentrate the lower order tensions of the chain 80 at the fourth order of the sprocket 30, thereby reducing the overall maximum tensions imparted to the chain 80 by the sprocket 30. Such use of a combination of random root radii and repeating root radii patterns that shifts tensions imparted to the chain 80 by the sprocket 30 also provides benefits in that the overall maximum chain tensions may be reduced, while also reducing chain noise or whine.
As illustrated in
The arrangement of the root radii may be selected by substantially repeating the root radii pattern a number of times equal to the sprocket order at which it is desired to concentrate the chain tensions. For instance, to concentrate the tensions imparted to the chain 80 by the sprocket 30 of the invention at the fourth sprocket order, the arrangement of the root radii may comprise a pattern that substantially repeats four times around the sprocket 30.
As shown in the chart 60 and Table 2, the sprocket 30 of
For example, the first, second, and third sprocket orders for the sprocket 30 of
As mentioned above, the random and repeating root radii pattern can provide the benefit of reducing the overall maximum tensions imparted to the chain 80 by the sprocket 30, while also reducing noise generated by contact between the sprocket 30 and the chain 80. The expected overall maximum tension reducing effects of the random sprocket 30 of the invention are illustrated in
As illustrated in
The maximum tensions imparted to the chain 80 by the random sprocket 30 designed for both noise reduction and reduced maximum chain tensions are expected to be significantly lower than for the random sprocket 20 designed principally to reduce noise. In fact, the tension reducing sprocket 30 may impart comparable, and in some instances, lower maximum tensions to the chain 80 than the straight sprocket 10 at engine speeds reflected in
Although the fourth order was selected in the aspect of the invention illustrated in
In addition, the tensions imparted to the chain 80 by the sprocket may be concentrated at more than one sprocket order. For example, a root radii pattern may be selected that has a major root radii sequence repeating twice for each revolution of the sprocket and a minor sequence that repeats twice within each major sequence. Thus, in this aspect of the invention, the major and minor radii are provided by having the minor pattern repeating within the major repeating pattern. A benefit of having both major and minor repeating patterns is the ability to further redistribute the sprocket orders at which tensions imparted to the chain 80 by the sprocket occur.
Thus, for every revolution of a sprocket having such a pattern, the major root radii sequence may impart two tensioning events, while the minor root radii sequence may impart four tensioning events. The tensioning events imparted by the minor root radii sequence may be of a lesser magnitude than the tensioning events imparted by the major root radii sequence.
Chain tensions, in addition, may be imparted to the chain 80 by various parts of the automotive engine system external to the sprockets, such as the shaft, the pistons, and/or chain tensioners. Chain tensions further may vary according to the operating temperature of the system. For example, when the ambient temperature of the engine decreases, the chain 80 may tend to cool and then contract, resulting in an increased chain tension. Conversely, when the ambient temperature of the engine increase, the chain 80 may tend to expand, thereby decreasing the tension in the chain 80. These external sources may impart tension events to the chain 80 in addition to those imparted to the chain 80 by the sprockets 20 and 30 of the above examples. These external tensioning events may occur at intervals that correspond to orders of the sprocket revolution.
In order to reduce overall chain tensions in the chain and sprocket system, the tensions imparted to the chain 80 by the improved random and repeating root radii pattern of the invention, such as those of sprocket 30, may be selected to at least partially offset tensions imposed on the chain 80 by such sources external to the sprocket 30 and chain 80. In one aspect of the invention, the orders of the sprocket revolution corresponding to peaks in the chain tension due to external sources, as well as those due to the sprocket 30, are determined. The sprocket 30 is then configured to concentrate chain tensions at a sprocket order at which the chain tensions due to external sources are at a minimum. This provides the potential to reduce the overall tensions in the chain 80, such as may occur if both the chain tension due to the sprocket 30 and the chain tension due to external sources are at their maximums.
In another aspect of the invention, the sprocket 30 is configured to impart maximum tensions to the chain 80 at orders that add to tensions imparted by external sources. This provides the ability to concentrate the maximum chain tensions due to both the sprocket 30 and the external sources at a predetermined sprocket order.
For example, when the external tensions occur four times for every rotation of the sprocket 30, the root radii of the sprocket 30 may be arranged to concentrate the maximum tensions imparted to the chain 80 by the sprocket 30 at sprocket orders phased to at least partially cancel the external tensions imparted to the chain. In this manner, the external tensions in the chain 80 may be at least partially offset by the sprocket tensions in the chain 80 to reduce the overall tension in the chain 80 and increase the life cycle of both the chain 80 and the sprocket 30.
In another aspect of the invention, the sprocket 30 is configured to impart increased chain tensions at one or more predetermined orders to generate low order tension fluctuations. The low order fluctuations may be used to help actuate a variable cam timing unit.
From the foregoing, it will be appreciated that the invention provides a method and apparatus for reducing noise generated by the engagement between a chain and a sprocket, while reducing the tensions imparted to the chain by the sprocket. While the figures are illustrative of aspects of the invention, the invention is not limited to the aspects illustrated in the figures. Furthermore, the invention is not limited to the aspects described herein above or to any particular aspects.
|Cited Patent||Filing date||Publication date||Applicant||Title|
|US515449||27 Feb 1894||Bicycle|
|US530058||20 Jun 1893||27 Nov 1894||Driving-gear for bicycles|
|US571086||10 Nov 1896||Pump-power|
|US596289||31 Aug 1896||28 Dec 1897||William thomas smith|
|US611170||16 Nov 1897||20 Sep 1898||James howard|
|US613756||24 Nov 1897||8 Nov 1898||Sprocket-wheel|
|US1650449||15 Apr 1925||22 Nov 1927||Max Jaeger||Positive variable-speed transmission|
|US1936117||7 Jul 1927||21 Nov 1933||Peschl Frank A||Variable-speed power-transmitting mechanism|
|US1963314||20 Apr 1933||19 Jun 1934||Baker Perkins Co Inc||Swinging-tray conveyer|
|US2344757||29 Sep 1942||21 Mar 1944||Weisberger Irving||Bicycle|
|US2477441||19 Oct 1946||26 Jul 1949||Leonard W Cole||Toy gear|
|US2941413||22 Jan 1957||21 Jun 1960||Dayco Corp||Power transmission belts|
|US3583250||1 Apr 1969||8 Jun 1971||Rca Corp||Transmission including toothed belt and partially toothed pulley|
|US3752035||5 Apr 1971||14 Aug 1973||Gen Electric||Auto-synchronizing gear system|
|US3752601||22 Sep 1971||14 Aug 1973||Ford Motor Co||High pressure liquid pump|
|US3830212||24 Jul 1973||20 Aug 1974||Yamaha Motor Co Ltd||Chain-sprocket transmission means in piston-crank mechanism|
|US3858454||12 Oct 1973||7 Jan 1975||T K F Inc||Conveyor drive mechanism|
|US3899932||19 Dec 1973||19 Aug 1975||Roger Owen Durham||Chain retention device for elliptical sprockets|
|US4036071||2 Apr 1976||19 Jul 1977||Hollis And Company||Sprocket and method for producing same|
|US4168634||27 May 1977||25 Sep 1979||General Motors Corporation||Chain and sprocket power transmitting mechanism|
|US4181034||27 Apr 1978||1 Jan 1980||Jacques Daniel||Chain drive means for a bicycle or the like|
|US4193324||27 Dec 1977||18 Mar 1980||Clint, Inc.||Bicycle sprocket drive apparatus with elliptical pedal path|
|US4337056||17 Nov 1980||29 Jun 1982||Uniroyal, Inc.||Mechanical power transmission system|
|US4504074||8 Jun 1983||12 Mar 1985||Upright, Inc.||Steering system|
|US4515577||20 Oct 1982||7 May 1985||Uniroyal, Inc.||Low backlash-high-torque power transmission system and toothed belt used therein|
|US4522610||23 May 1983||11 Jun 1985||Shimano Industrial Company Limited||Gear crank apparatus for a bicycle|
|US4526558||3 Nov 1983||2 Jul 1985||Durham Roger O||Chain engagement slot for bicycle sprockets|
|US4810237||8 Sep 1986||7 Mar 1989||Urpo Mantovaara||V-belt pulley and drive|
|US4865577||8 Sep 1988||12 Sep 1989||Trustees Of Columbia University In The City Of New York||Noncircular drive|
|US4913684||17 Jun 1987||3 Apr 1990||Variped Oy||Automatic variable transmission for vehicles|
|US4915598||3 Feb 1989||10 Apr 1990||Man Nutzfahrzeuge Gmbh||Auxiliary drive of an internal combustion engine for an air compressor|
|US4936812||5 Aug 1988||26 Jun 1990||The Gates Rubber Company||Torque reactive tension mechanism and method|
|US5267910||29 Jan 1993||7 Dec 1993||Tsubakimoto Chain Co.||Silent chain having improved noise reduction|
|US5394282||18 Nov 1993||28 Feb 1995||Nec Corporation||Cartridge holding mechanism for magnetic tape cartridge apparatus|
|US5397280||4 Oct 1993||14 Mar 1995||Borg-Warner Automotive, Inc.||System phasing of overhead cam engine timing chains|
|US5427580||4 Oct 1993||27 Jun 1995||Borg-Warner Automotive, Inc.||Phased chain assemblies|
|US5437581||25 Oct 1994||1 Aug 1995||Borg-Warner Automotive, Inc.||Phased chain assemblies|
|US5453059||3 Aug 1994||26 Sep 1995||Borg-Warner Automotive, Inc.||Variable pitch silent chain|
|US5490282||8 Dec 1992||6 Feb 1996||International Business Machines Corporation||Interface having serializer including oscillator operating at first frequency and deserializer including oscillator operating at second frequency equals half first frequency for minimizing frequency interference|
|US5492390||20 Apr 1994||20 Feb 1996||Nudvuck Enterprises||Variable shaped wheel|
|US5549314||7 Oct 1994||27 Aug 1996||Sassi; Michel||Non-circular front chain wheel for crank gear|
|US5551925||21 Dec 1994||3 Sep 1996||Borg-Warner Automotive, Inc.||Chain assemblies with minimal pin projection|
|US5562557||19 Oct 1995||8 Oct 1996||Borg-Warner Automotive, Inc.||Phased chain assemblies|
|US5611744||20 Feb 1995||18 Mar 1997||Sichuan Xinxin Mechanical Engineering Co., Ltd.||Bicycle crank driven chain wheel assembly|
|US5628702||30 Aug 1995||13 May 1997||Borg-Warner Automotive, K.K.||Power transmission chain|
|US5683319||2 May 1996||4 Nov 1997||Borg-Warner Automotive, Inc.||Chain assemblies with minimal pin projection|
|US5772546||13 Sep 1996||30 Jun 1998||Warszewski; Jaroslaw Piotr||Continuously variable automatic drive|
|US5816967||19 Jun 1996||6 Oct 1998||Borg-Warner Automotive, Inc.||Phased chain assemblies|
|US5846149||10 Sep 1997||8 Dec 1998||Borg-Warner Automotive, Inc.||Phased chain assemblies|
|US5876295||23 Jan 1997||2 Mar 1999||Cloyes Gear And Products, Inc.||Roller chain drive system having improved noise characteristics|
|US5882025||1 Feb 1996||16 Mar 1999||Runnels; David J.||Bicycle with rhombus-like gear with circularly curved apexes|
|US5935046||25 Mar 1998||10 Aug 1999||Maresh; Joseph D.||Variable motion elliptical exercise machine|
|US5971721||27 Mar 1998||26 Oct 1999||Thermo Fibertek Inc.||High pressure pump having an eccentric transmission|
|US5976045||25 Jul 1997||2 Nov 1999||Cloyes Gear And Products, Inc.||Random engagement roller chain sprocket having improved noise characteristics|
|US6019692||21 Apr 1997||1 Feb 2000||Mitsubishi Jidosha Kogyo Kabushiki Kaisha||Belt drive device for reducing belt load|
|US6050916||6 May 1999||18 Apr 2000||Volkswagen Ag||Toothed belt or chain drive arrangement having a tooth with different flank geometry from other teeth|
|US6155943||15 Sep 1998||5 Dec 2000||Borgwarner Inc.||Randomized sprocket for roller chain|
|US6189639||1 Jul 1998||20 Feb 2001||Honda Giken Kogyo Kabushiki Kaisha||Chain roller structure in chain driven vehicle|
|US6213905||30 Jul 1999||10 Apr 2001||Borgwarner Inc.||Roller chain sprockets oriented to minimize strand length variation|
|US6736744||1 Nov 2000||18 May 2004||Borgwarner, Inc.||Roller chain sprocket for preventing substantially radial impact with chain rollers|
|US7125356||6 Nov 2001||24 Oct 2006||Borgwarner Inc.||Tension-reducing random sprocket|
|US7654925||10 Jul 2006||2 Feb 2010||Borgwarner Inc.||Tension-reducing random sprocket|
|US20010023212||15 Mar 2001||20 Sep 2001||Hiroshi Horie||Low noise silent chain|
|US20020142873||4 Jan 2002||3 Oct 2002||Jorg Oser||Chain drive arrangement|
|US20020169043||7 May 2002||14 Nov 2002||Chieh-I Liu||Elliptic gearing for a bicycle|
|US20030104886||15 Nov 2002||5 Jun 2003||Witold Gajewski||Synchronous drive apparatus and methods|
|DE2014537A1||25 Mar 1970||15 Oct 1970||Title not available|
|DE2338865A1||31 Jul 1973||21 Feb 1974||Yamaha Motor Co Ltd||Zahnkettentriebwerk|
|DE3739336A1||20 Nov 1987||1 Jun 1989||Goetze Ag||Internal combustion engine with a vibration-damped camshaft drive|
|DE4241231A1||8 Dec 1992||9 Jun 1994||Wilfried Rahe||Contact belt gear box with periodically changing translation - has two or more discs with fixed rotary axes looped by contact belt of constant length in each position of discs.|
|DE4316877A1||19 May 1993||25 Nov 1993||Borg Warner Automotive||Sound-proofed chain drive for torque converters and vehicle parts - has several sets of overlapping plates with inverted teeth connected by bolts and driven by multi-part chain wheel.|
|DE4331482A1||16 Sep 1993||24 Mar 1994||Luk Lamellen & Kupplungsbau||Chain or toothed belt drive for driving valves in IC engines - has irregular divisions on chain wheels interacting with different length chain links|
|DE19520508A1||3 Jun 1995||5 Dec 1996||Audi Ag||Control belt or timing drive for IC engine|
|DE19649397A1||29 Nov 1996||4 Jun 1998||Boerger Gmbh||Operating positive displacement pump to transport medium|
|DE19812939A1||24 Mar 1998||14 Jan 1999||Mitsubishi Motors Corp||Nockenwellenantriebsvorrichtung|
|DE20008042U1||4 May 2000||17 Aug 2000||Schlosmacher Dietmar||Elliptischer Antrieb für Fahrzeuge und Trimmgeräte aller Art|
|EP0066294A1||2 Jun 1982||8 Dec 1982||R.V.T. DESIGN & ENGINEERING LIMITED||Transmission|
|EP1448916B1||24 Oct 2002||2 Aug 2006||Litens Automotive||Synchronous drive apparatus with non-circular drive elements|
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|1||Analysis of Nonlinear Oscillations of the Timing Belt (1st Report, Regions of Resonance of the Timing Belt); Authors: Shao-chang Li, Hideyuki Otaki, Yoshio Ishikawa, Keiichi Watanuki; Nippon Kikai Gakkai Ronbunshu, C Hen/Transactions of the Japan Society of Mechanical Engineers, Part C, 1993, vol. 59, No. 568, Dec. 1993, pp. 3902-3906 (English Abstract only), 1 page.|
|2||Analysis of Nonlinear Vibration of Timing Belt: (Under Meshing Impact and Varying Tension by Eccentric Pulley) Authors: Shaochang Li; Hideyuki Otaki; Keiichi Watanuki; Conference Title: Proceedings of the 1995 Joint ASME/JSME Pressure Vessels and Piping Conference, 9 pages.|
|3||Audible Noise Produced by the Sporadic Changes of Tensile Forces in a Belt Driven System; Author: C. Ozturk; Journal of Low Frequency Noise & Vibration; 1995, vol. 14, No. 4, pp. 193-211 (English Abstract only), 1 page.|
|4||Base and Application of Timing Belt, Primary Part 5. Rotation Transmitting Error (Case of No Load); Authors: Tomio Koyama; Masanori Kagotani; Kikai no Kenkyu (Science of Machine), 2003, vol. 55, No. 2, pp. 269-278 (English Abstract only), 1 page.|
|5||European Patent Office Search Report for European Patent Application No. 02257611, dated Dec. 6, 2004, 3 pages.|
|6||Life Analysis of Water Pump Bearing for Cars Considering Shaft Rigidity; Authors: Masaaki Sakuragi; Shigeo Kamamoto; Koyo Eng J, 1989, No. 136, pp. 51-63 (English Abstract only), 1 page.|
|7||Nonlinear Vibration Analysis of Running Viscoelastic Belts; Author: YS Choi; Proceedings of the 5th International Conference on Vibration Engineering; Nanjing, China, Sep. 18-20, 2002 (English Abstract only), 1 page.|
|8||Parametric Excitation of Timing Belt; Author: Eiki Osaki; Nippon Hakuyo Kikan Gakkaishi (Journal of the Marine Engineering Society in japan); 1993, vol. 28, No. 5, pp. 320-325 (English Abstract only), 1 page.|
|9||Parametric Instability of Belts: Theory and Experiments; Authors: F. Pellicano (Reprint); G. Catellani; A. Fregolent, Computers & Structures, Jan. 2004, vol. 82, No. 1, pp. 81-91 (English Abstract only), 1 page.|
|10||Primary and Parametric Non-Linear Resonances of a Power Transmission Belt: Experimental and Theoretical Analysis; Authors: F. Pellicano; A. Fregloent; A. Bertuzzi; F. Vestroni; Journal of Sound and Vibration, Jul. 19, 2001, vol. 244, No. 4, pp. 669-684 (English Abstract only), 1 page.|
|11||Study on a Servo Control System Using Timing Belt Drives; Authors: H. Lee, Tatsuaki Masutomi, Naoyuki Takesue, Masamichi Sakaguchi, Junji Furusho, Hideaki Tanaka; Proceedings of the Annual Conference of the Institute of Systems Control and Information Engineers, 2000, vol. 44th, pp. 625-626 (English Abstract only), 1 page.|
|12||Study on Timing Belt Noise (How to Reduce Resonant Noise) Conference Title: Proceedings of the 1989 International Power Transmission and Gearing Conference: New Technologies for Power Transmissions of the 90's; Chicago, Illinois, Apr. 25, 1989, 9 pages.|
|13||Vibration and Control of Axially Moving Belt System (Effect of Inclined Angle by Theory and Experiment); Authors: Yoshi Hirase; Kouetsu Takano; Hiroki Okubo; Osami Matsushita; Keiji Watanabe. Nippon Kikai Gakkai Kikai Rikigaku, Keisoku Seigyo Koen Ronbunshu, 1999, vol. 1999, No. A, pp. 443-446 (English Abstract only), 1 page.|
|14||Vibration and Control of Axially Moving Belt System, 1st Report, Experimental Analysis; Authors: Takano Koetsu; Keiji Watanabe; Osami Matsushita; Masanori Kitano; Nippon Kikai Gakkai Ronbunshu. C (Transactions of the Japan Society of Mechanical Engineers, C), 1998, vol. 64, No. 618, pp. 421-428, Fig. 20, Tbl. 6, Ref. 8, with English Translation, 36 pages.|
|15||Vibration and Control of Axially Moving Belt System, 3rd Report, Analysis by Parametric Excitation; Authors: Hiroki Okubo; Koetsu Takano; Osami Matsushita, Keiji Watanabe, Yoshi Hirase; Nippon Kikai Gakkai Ronbunshu. C (Transactions of the Japan Society of Mechanical Engineers. C), 1999, vol. 65, No. 635, pp. 2706-2712, with English Translation, 34 pages.|
|16||Vibration and Control of Axially Moving Belt System. 4th Report. Effect of Inclined Angle by Experiment; Authors: Koetsu Takano; Yoshi Hirase; Hiroki Okubo; Osami Matsushita; Keiji Watanabe; Nippon Kikai Gakkai Ronbunshu. C (Transactions of the Japan Society of Mechanical Engineers. C), 2000, vol. 66, No. 645, pp. 1439-1444 (English Abstract only), 1 page.|
|17||Vibration and Control of Axially Moving Belt System. Effect of Inclined Angle; Authors: Yoshi Hirase; Kouetsu Takano; Hiroki Okubo; Osami Matsushita; Keiji Watanabe. Nippon Kikai Gakkai Kikai Rikigaku, Keisoku Seigyo Koen Ronbunshu, 1998, vol. 1998, No. B, pp. 317-320 (English Abstract only), 1 page.|
|18||Vibration and Control of Axially Moving Belt System: Analysis and Experiment by Parametric Excitation; Authors: H. Okubo (Reprint); K. Takano; O. Matsushita; K. Watanabe; Y. Hirase; Journal of Vibration and Control, May 2000, vol. 6, No. 4, pp. 589-605 (English Abstract only), 1 page.|
|19||Vibration and Control of Axially Moving Belt System: Analysis and Experiment by Parametric Excitation; Authors: H. Okubo; K. Takano; O. Matsushita; K. Watanabe; Y. Hirase; Journal of Vibration and Control, May 2000, vol. 6, No. 4, pp. 589-605.|
|20||Vibration Induced in Driving Mechanism of Photoconductor Drum in Color Laser Printer; Authors: Hiroyuki Kawamoto; Yosuke Watanabe; Nippon Kikai Gakkai Kikai Rikigaku, Keisoku Seigyo Koen Ronbunshu, 2000, vol. 2000, No. Pt 4, pp. 1028-1031 (English Abstract only), 1 page.|
|21||Vibration of Timing Belt Subjected to Fluctuations of Tension; Authors: Eiki Osaki, Yoshihiro Miyoshi; Katsuyuki Koga; Journal of National Fisheries University; 1996, vol. 45, No. 2, pp. 79-85 (English Abstract only), 1 page.|
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|US20100167857 *||20 Jun 2007||1 Jul 2010||Borgwarner Inc.||Resonance tension reducing sprocket with combined radial variation and sprocket wrap|
|US20100292038 *||26 Dec 2007||18 Nov 2010||Borgwarner Inc.||Multiple Tension Reducing Sprockets in a Chain and Sprocket System|
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|U.S. Classification||474/152, 474/156, 474/160|
|International Classification||F16H7/06, F16H55/30|
|Cooperative Classification||F16H2055/306, F16H55/30|
|11 May 2011||AS||Assignment|
Owner name: BORGWARNER INC., MICHIGAN
Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:TODD, KEVIN B.;REEL/FRAME:026259/0136
Effective date: 20110510
|24 Apr 2015||FPAY||Fee payment|
Year of fee payment: 4